CA2329764C - Installation for the construction of batches of articles - Google Patents

Abstract

The packaging conveyor for bottles has a conveyor belt (2) with multiple pushers (6) spaced regularly along it on a movable support (7). The pushers move in a closed path which extends in a plane (P) perpendicular to the conveying surface (S) and locally contiguous to it. Each pusher is movable between inactive and active positions. In the latter, the pusher extends from the conveying surface to engage an article to be pushed (3). The number of pushers active at any time can be varied. The conveyor belt speed changes can be pre-programmed.

Description

The invention relates to a packaging installation for forming finished products such as packs from lots of items.

The invention applies in particular to the packaging of articles such as bottles or cans, generally of cylindrical shape.

It is known that articles are first sent individually to a feeding way to a grouping station where batches of articles are trained then spaced to be transferred to an escape route along which they are packaged, or packaged.

To form a space between two batches of successive articles, it is known speed up the batch of items between the feed path and the track discharge.
We can notably cite the document GB-974 995.

The space then formed between the same faces of two consecutive lots is called not or not machine.

2o Due to the conservation of the flow of the machine, it is easy to establish enter here linear output speed of an article and its speed of entry, the relationship next :
VS = VE x L (1) where VS is the exit speed of the article, VE its entry speed, P step machine and L the length of a lot of items.
Distributors are currently seeking to reduce their inventories while offering increasingly diversified ranges of packaged products.

As a result, the throughput of the packaging machines must be continually revised upward. Thus, in the field of packaging bottles or cans, there are currently order from 15,000 to 100,000 bottles per hour.

2 In addition, distributors demand to be able to vary their offer within a same range of products, by offering consumers, for a single such as a bottle or a can of drinks, varied packaging such as packs of two, three, four, six, of eight or more articles.

In order to meet these requirements, builders must be able to constantly renew their ranges of machines, so as to adapt them not only to the shapes of the new products, their sizes, their weights, But also the size and shape of their packaging, most often blanks cardboard or equivalent.

Currently, manufacturers offer distributors solutions or packaging machines that have many disadvantages.
Some manufacturers offer distributors a machine for each type of finished product, which is heavy and expensive.

Other manufacturers offer a machine for each range 2o of product, which requires adjusting the machine according to the type of desired packaging: lots of two, four, six, eight, or more.

Indeed, at constant machine flow (therefore at constant input speed), there is location to adapt the output speed and / or the machine pitch, by the relation recalled above.

Most machines do not have a pitch control system. he it is therefore necessary to increase the exit speed, the step being fixed than the number of articles per lot.

For example, to switch from batch grouping of twelve items to one batch grouping of four requires tripling the output speed of the machine, which is incompatible with the physical limits of the installations, and in particular packaging devices.

3 Some machines have manual pitch control systems.
which requires as many manual interventions as there are changes in product within the same range.

At present, the frequency of these changes can reach two to three per day, frequency difficult to reach through manual adjustments.
The invention aims to solve, in particular, the aforementioned drawbacks of the art prior, by proposing an installation that allows the adjustment automatic to the times the number of items per lot, the step machine, and the rate of production.

For this purpose, the object of the invention is a packaging installation form 15 finished products such as packs from batches of articles, which includes:

a conveyor capable of receiving the batches of successive articles for the to convey from a so-called upstream location to a so-called downstream location, the upstream faces of two successive batches being spaced apart a distance 20 predetermined said not;
- a route of advancement along which the items are routed one to one towards the said conveyor being juxtaposed to each other;
means for transferring articles from the advancement path to the Conveyor, able to take and group items to form batches 25 spaced apart;
- A carrier capable on the one hand to route one by one cardboard blanks or equivalent, laid substantially flat on the conveyor, towards the said conveyor, and to arrange the blanks on the conveyor opposite the lots articles;
Conveyor drive means, transfer means and carrier.
The installation is characterized in that it comprises a device for command and control of the drive means, adapted to apply to

4 each drive means a speed profile selected from a set pre-programmed speed profiles, to allow the setting of the pitch and / or of number of articles in batches according to the step and / or batch type desired.

Each type of conditioning corresponds to a speed profile for each driving means.

By programming these speed profiles in advance, it is therefore possible to pass automatically from one to the other, so that the setting of the machine is easy and fast.

It is thus possible to switch immediately from one type of packaging to another, for example from a batch packaging of eight to one batch conditioning of four, maintaining the output speed constant.

According to one embodiment, this installation furthermore comprises:
means adjacent to the progress path and the transfer means, able to order and clock items from the track of progress so that they present the positioning and the spacing wanted at the moment of their prehension by the means of transfer; and a means of training means for ordering and timing the articles, slaved to the control device.

According to one embodiment, said transfer means comprise a toothed wheel at least a portion of which is pivotally mounted about an axis of rotation, this wheel being disposed close to the feed path and of the escape route, substantially tangent thereto, this wheel comprising the said gripping members.

The gripping members are for example in the form of teeth substantially regularly spaced, projecting radially from the toothed wheel, each tooth describing a circle passing through a first angular position wherein it engages at least one article at the feeding station, and a second angular position in which it disengages the latter at the station discharge.

According to one embodiment, the wheel comprises a circular fixed base and a rotating disk, coaxial and superimposed, between which are arranged of the radial branches whose free ends form the said teeth.

According to a particular constructive provision, the said branches are mounted rotated on the disk by means of axis pivots parallel to the axis of the wheel.
For example, each branch comprises a roller or a pin that cooperates with a groove in the base, this groove being extended in a closed loop around the axis of rotation of the wheel.

This groove is arranged so that:
- when passing the tooth through the feeding station, the branch that door pivots in the opposite direction of the rotation of the wheel so that the tooth speed decreases to be substantially equal to the speed entry when the articles are entered;
- between the feeding station and the evacuation station, the orientation of said branch is constant with respect to the wheel so that the speed of the tooth increases to be substantially equal to the speed of the wheel, so that articles are grouped in batches, accelerated, spaced.
In addition, means may be provided near the post feeding, able to order and rate the items coming from the feeding way, so that they present the positioning and spacing wanted at the moment of their prehension by means of transfer.
According to one embodiment, said carrier comprises pushers of blanks successively arranged on the conveyor, each pusher being adapted to come into contact with a blank to convey it to the conveyor, the distance enter two successive pushers engaged with a blank being predetermined and substantially equal to the pitch.

We can also provide:
means for adjusting the distance between two successive pushers taken with a blank according to a predetermined value selected from a group pre-programmed values, all multiples of the same value module.
a means for driving the adjustment means, slaved to the device of ordered.

According to one embodiment, the control device is arranged to apply to at least one of the training means, and for example to each drive means, a predetermined speed profile selected from a 1s pre-programmed set of speed profiles.

For this purpose, the or each drive means may comprise an engine whose rotation speed is continuously adjustable, such as an engine electric, brushless DC type.

Other objects and advantages of the invention will become apparent during the following description of embodiments, description made in reference in the accompanying drawings, in which:

FIG. 1 is a perspective view of a packaging installation whose setting is automated, this installation comprising in particular:
- a way to route items one by one;
means for clocking and orienting the articles placed in the vicinity from one end of this lane;
means for transferring articles from the route to a conveyor, which group the articles in batches by placing them on cardboard blanks or equivalent from a carrier;

means for unstacking the blanks from a stack to this carrier ;
means for setting the volume and closing of the blanks around the batches to form packs.
s FIG. 2 is a view of a detail of FIG. 1, illustrating a portion uphill the installation;

FIG. 3 is a view of a detail of FIG. 1, illustrating a portion downstream of the installation;

FIG. 4 is a perspective view of one embodiment of the means transfer of articles from the advancement path to the conveyor, as well as only means to order and clock the articles; the means of 15 transfer comprise a toothed wheel of which at least a portion is mounted pivoting device comprising a plurality of gripping members, while the ways to order and rate the items include a wheel starry also swivel;

FIG. 5 represents a sectional view from above of the transfer means represented in FIG. 4;

FIG. 6 is a view of a detail of FIG. 5, which shows the throat made in the base of the toothed wheel; in this figure a branch is Partially shown, its inner end facing the axis of the wheel, has a pebble circulating in the throat; the throat includes a portion with constant curvature and a portion with variable curvature; branch is represented in a position where its roller, which circulates for example clockwise, just left the portion to Variable curvature and is engaged in the portion with constant curvature; and FIGS. 7 and 8 are graphs representing the speed of an organ of gripper carried by a branch as shown in FIG.

function respectively of the angular position of the roller of the branch, and the angular position of the gripping member; in figure 7 are schematically represented as braces the portions of the grooves with which the roller successively cooperates during the rotation of the gear wheel on a lathe.

FIG. 9 is a perspective view of a conveying system comprising two parallel endless conveyors for routing flat objects such as cardboard blanks or the like; these carriers each comprise a plurality of articulated pushers adapted to be engaged by an adjustable rotary actuator;

FIG. 10 is a view of a detail of FIG. 9, which illustrates the pivoting a pusher engaged with the actuating member;
FIGS. 11 to 14 are longitudinal elevation views of the system of conveying of FIGS. 9 and 10, which illustrate four successive stages of pivoting a pusher from a so-called inactive position to a position.
active, according to a first setting of the actuating member, so that this last actuates one pusher on two;

FIGS. 15 to 18 are views similar to the views of FIGS. 11 to 14, who illustrate four successive stages of the pivoting of a pusher since a said inactive position to an active position, according to a second setting of the actuator, so that the latter actuates a pusher on three;

FIG. 19 is a diagram illustrating the evolution of the speed of rotation of the actuating member of the conveying system of FIGS. 9 to 18, in function of its angular position, according to a first setting where the organ actuator engages with one pusher on two (solid lines), according to a second setting where it comes into contact with one pusher on three (lines mixed), and according to a third setting where it comes into engagement with a pusher out of four (discontinuous traits).

FIG. 1 shows a packaging installation 1 of articles 2 such as bottles or cans, from which are formed finished products such as packs 3.
s Articles 2 are introduced at an entry point 4 of the installation 1, while the packs 3 are evacuated from an exit station 5.

To be packaged, articles 2 undergo a number operations which, for convenience, are supposed to take place in the same plane of substantially horizontal work M along a conveying path 6 represented by the arrows, which extends between the entry station 4 and the post of 5, substantially in a longitudinal direction L, shown in FIG.
the Figures 1 to 18.

In the figures is also shown a transverse direction T, substantially perpendicular to the longitudinal direction L being contained in the work plan M.

An elevation direction E is also shown. This direction is substantially vertical, perpendicular to the plane M, so that the directions longitudinal L, transverse T and elevation E form an orthogonal reference by report to which this description is made.

The terms upstream, downstream are defined in relation to the direction longitudinal; the lateral term is defined in relation to the direction transversal, while the terms up, down are defined relative at the elevation direction.

3 In this installation 1, articles 2 undergo two operations Main:
on the one hand the grouping in spaced batches 7, and on the other hand the packaging or packaging of batches 7 to form packs 3.

= 10 Each batch 7 comprises a predetermined number of aligned articles 2. This number can vary between 2 and 6, or more.

Each pack 3 includes at least a lot 7 of articles 2. For that-fe pack contains at least two parallel batches 7 of articles 2, it can be provided several convergent conveyor paths 6, to form series separated from successive batches 7 which are then grouped together.

The installation shown in FIGS. 1 to 3 is intended to form packs 3 lo comprising two identical batches 7 of aligned articles 2.

That is why there are provided two symmetrical conveying paths 6 by relative to a longitudinal elevation plan, for the formation of two series separate lots 7.

This representation is obviously given as an example, and we can provide a plurality of convergent separate conveying paths 6.

For each series of lots 7, the installation 1 comprises a device 8 for the 2o constitution of lots 7.

This device 8 comprises an advancement channel 9 which extends between the station 4 and an intermediate position 10 located between the entry station 4 and the output station 5, for example at a substantially equal distance from the latter.
Articles 2 are conveyed along the progress path 9, one by one, in being juxtaposed to one another by means of a motorized treadmill or of any other equivalent means.

3o the device 8 also comprises a conveyor 11 able to receive the batches successive articles 2 to forward them from an upstream location to near the intermediate station 10, to a downstream location near the exit station 5.

It When they are arranged on the conveyor 11, the batches 7 have a face facing upstream and one side facing downstream. The upstream faces of two successive batches 7 are spaced a predetermined distance P said not.

According to an embodiment illustrated in FIGS. 1 to 3, the conveyor 11 includes two endless 12 motorized endless carrier belts, extending longitudinally.

Moreover, the device 8 also comprises:
a drive means 13 of the conveyor 11;
means 14 for transferring articles 2 from the progress path 9 to the conveyor 11, able to take and group the articles 2 to form spaced lots; and a drive means 15 for the transfer means 14.
l5 The structure of this device 8 and its mode of operation will be described in detail later in the description.

Installation 1 is provided so that the pitch P, the number of items 2 per batch 7 and the 20 production rates are automatically adjustable.

These adjustments are made by applying in particular to the conveyor 11 and the transfer means 14 of the particular speed profiles via of their respective drive means 13, 15.

For this purpose, the installation 1 further comprises a control device 16 and servocontrol of the drive means 13, 15.

The control device 16 is arranged to apply to each means 3, in particular, a speed profile chosen from a together pre-programmed speed profiles.

The control device 16 comprises for example a computer memory 17 in which are stored sets of speed profiles intended for to be applied selectively to each of the drive means 13, 15.

The speed of each drive means 13, 15 may be a function of its angular position and / or time.

In order for Articles 2 to be presented at the moment of their transfer means 14, the desired positioning and spacing, the device 8 It can also include means 18 capable of ordering and timing the Articles 2 from the way forward 9.

According to one embodiment, the means 18 are adjacent to the track 9 and the transfer means 14.

The device 8 further comprises a drive means 19 of the means 18 to order and clock the articles 2, slaved to the control device which can apply to the driving means 19 a speed profile predetermined, chosen, as before, from among pre-set programmed speed profiles.

The speeds of the driving means can be variable during the time, training means 13, 15, 19 adapted to such variations.
For this purpose, at least one of the drive means 13, 15, 19; especially the drive means 15 of the transfer means 14, comprises a motor 20 whose rotation speed is continuously adjustable.

This motor 20 is for example a DC electric motor without brooms, more commonly called brushiess motor, whose speed of rotation can be modulated at will.

The brushiess motors are known and are already the subject of numerous applications in the industry.

Their main advantages are on the one hand a variable speed of rotation in depending on the voltage applied to their terminals, and on the other hand a long life increased by the absence of brushes and commutators, sources of friction and wear.

In order to form the packs 3, the installation 1 also comprises means lo packing 21 of lots 7 of articles 2.

According to an embodiment illustrated in FIGS. 1, 2, 9, 10, the installation 1 comprises a conveyor system 22, which comprises;

a conveyor 23 extended substantially longitudinally, which conveys a by one of the cardboard blanks 24 or equivalent to the intermediate position 10 for arranging them on the conveyor 11 opposite lots 7 of articles 2;
a drive means 25 of said conveyor 23, slaved to the device of order 16.

The blanks 24 comprise for example a central panel on which are intended to be arranged articles 2, and around which are articulated side panels and parts holding shutters 2.

The blanks 24 are laid flat on the conveyor 23, being extended transversely in the plane M (Figure 9).

According to an embodiment illustrated in FIGS. 1, 2 and in the figures 9 to 18, the conveyor 23 comprises pushers 26, each being able to come into taken with a blank 24 to convey it to the conveyor 11.

The control device 16 comprises for example a computer memory 17 in which are stored sets of speed profiles intended for be applied selectively to the training means 25 and to each of the possible other means of training.

According to the intended operation for each of these training means, one introduced into the control device 16, by programming in the memory 17, constant or variable speed profiles as a function of time.

The control device 16 is thus arranged to apply to the means in particular, a speed profile chosen from a set pre-programmed speed profiles, introduced in the memory 17.
The drive means 25 is selected so that it can be applied to constant velocity profiles, the velocity profile being modified during a change of pace for example.

For this purpose, it comprises for example a motor whose rotation speed is variable and continuously adjustable. This engine is for example electric to Brushless direct current, called brushiess motor.

An unstacking device 27 may be provided for transferring the blanks 24.
since a stack 28 towards the conveyor 23, as well as a drive means 29 of the unstacking device 27, slaved to the control device 16.

According to an embodiment illustrated in FIGS. 1 and 2, the device of unstacking 27 comprises a rotary drum 30 of transverse axis to which are fixed pivotally transverse arms 31 substantially parallel and regularly spaced.

The arms 31 are associated with the drum in the vicinity of its periphery 32, and include suction cups 33 capable of sucking the blanks 24 and transferring them 3o from the stack 28 to the carrier 23, which in turn carries them to the convoyeurll.

The packs 3 are formed from batches 7 of articles 2 and blanks 24 to way including a folding device 34, adjacent to the conveyor 11, provided for fold the blanks holding the blanks.

For this purpose, the folding device 34 comprises a first rotary arm adjacent to the conveyor 11, rotating at a non-constant speed about an axis transverse passing substantially through the center of gravity of the arm 35.

The first arm 35 is symmetrical with respect to its axis and comprises, at the proximity of each of its ends, a curved portion 36 such that the arms 35 has substantially the shape of an S in a longitudinal elevation plane.

The arm 35 is rotated at a speed such that each half-turn of arm 35 coincides with the passage of a blank 24.

One of the curved portions 36 then engages with a flap 24a of the blank turned upstream, to bend it towards items 2 of lot 7 as and measuring the progress of the latter on the conveyor 11. -According to one embodiment, the speed of rotation of the arm 35 is constant and varies according to its angular position- around its axis.
In particular, the speed of the arm is substantially constant when the part curved 36 is engaged with the blank 24, while it is increasing then decreasing, or conversely according to the setting of the pitch P, between two passages successive of a blank 24.

The first arm 35 is rotated by a first means drive 37, slaved to the control device 16.

Moreover, the folding device 34 may also comprise a second rotating arm 38 adjacent to the conveyor 11, similar to the first arm, and arranged downstream of it, symmetrically with respect to an elevation plane transverse, so that the second arm 38 has substantially the shape of a Z
in a longitudinal elevation plane.

The operation of the second arm 38 is substantially identical to that of the s first, its rotational speed being however significantly different, from so that it ensures the folding of a shutter facing downstream.

The second arm 38 is also rotated by a second means 39, also controlled by the device 16 control.
According to one embodiment, a device 40 is also provided.
in volume of blanks 24 around batches 7 of articles 2.

This device 40, adjacent to the conveyor 11 downstream of the folding device 34 described above, is intended to fold the side panels of the blanks 24.

The setting device 40 includes a lever 41 in motion back-and-forth in a longitudinal elevation plane from bottom to top and reciprocally (Figure 3).

This lever 41 in motion pushes the side panels of the blanks 24 towards the up as the lot 7 of items 2 advance on the conveyor to reduce them to Articles 2 and partly to ensure the closure of the pack 3.

This lever 41 is driven at a predetermined speed in its movement of va and comes by a driving means 42 controlled by the control device 16.
A device 43 for closing the blanks 24 around the batches 7 to form the packs 3 is also planned.

This device 43 is for example disposed above the conveyor 11, and comprises a lever 44 with a transverse movement back and forth, for engage with a closure panel 45 of the blank 24 and fold down this last one against Articles 2 of Lot 7.

This lever 44 is set in motion at a predetermined speed by a means 46 of the closing device 43, which is slaved to the device order 16.
s The operating speeds of the drive means 42, 46, are predetermined, by being pre-programmed in the memory 17 of the device of order 16.

In addition, the installation 1 may comprise a guiding device 47 lots 7 along at least part of the conveyor 11, this device comprising by for example at least one endless belt 48 traveling along the conveyor 11.

The or each endless band 48 is driven in motion at a speed Predetermined by a drive means 49 of the guide device 47, controlled by the control device 16.

In order to ensure a continuous and synchronized operation of the installation 1, he is necessary to synchronize its different training means.

Each drive means controlled by the control device 16 corresponds to a predetermined set of velocity profiles introduced into the memory 17.

According to the intended operation for each of these training means, one introduced into the control device 16, by programming in the memory 17, constant or variable speed profiles as a function of time.
Examples of speed profiles are given later in particular for the drive means 15 of the transfer means 14.

The drive means 25, 29, 37, 42, 46, 49 are chosen so that Variable speed profiles can be applied to them.

For this purpose, at least one of them, and for example each of them, comprises a motor 20 such as that mentioned above, for example a brushiess engine.

Device 8 is now described in more detail with reference to FIGS.
8 to 18.

This device 8 comprises a feed path, or advancement path 9 the along which items 2 are routed one by one to a post 109, located in a grouping area 115, and for example confused with one end of the feeder lane 9.

Articles 2 are conveyed at a VE entry speed substantially constant along the feed path 9, being juxtaposed to each other at others, by means of a motorized treadmill or any other means equivalent.

The device 8 also comprises an escape route or conveyor 11, able to receive, at an evacuation station 111 located in the groupage area 115, items 2 grouped in batches 4 to 'route them from upstream to downstream at, a so-called output speed VS substantially constant, greater than the VE entry speed.

The device 8 further comprises transfer means 14 of the articles 2 from the supply station 109 to the evacuation station 111, which take items 2 at feed station 109 and group them together into batches spaced.

The transfer means 14 are arranged so that the number of articles 2 per lot 4 be variable without stopping the scrolling of the articles.

For this purpose, according to one embodiment, the transfer means 14 comprise a rotatable member adapted to take and group the articles 2 for forming batches 4 spaced apart, said rotary member comprising a succession of gripping members 113 which engage the articles 2 at the station power 109 and disengage them at the evacuation station 111 after they have been grouped in batches 4 and spaced.

The rotary member makes it possible to vary the number of items 2 per batch.
Between the supply station 109 and the evacuation station 111, the articles 2 are driven continuously along a closed path along a path that at least a quarter of the periphery of the rotary member, so that the gripping members 113 may come into contact with the articles and the io group in successive batches 4.

The speed of the rotary member is greater than the entry speed VE of the items.
The gripping members 113 are driven and circulate along a closed loop trajectory at a so-called transfer speed VT.

This transfer speed VT is greater than or equal to the entry speed VE
so that the items are accelerated between the feed station 109 and the evacuation station 111.

The VE input and VS output speeds being predefined, the means of transfer 14 are arranged so that the transfer speed VT of the organs of gripping 113 varies along their path, so that - when securing articles 2 to feed station 109, the speed transfer VT is substantially equal to the input speed VE;

- when transferring articles 2, that is between the feeding station and the evacuation station 111, the transfer speed VT is greater than the VE entry speed; and - when disengaging articles 2 at evacuation point 111, the speed transfer VT is substantially equal to the output speed VS.

Thus, the commitment and release of items 2 is done without shock and smoothly.

5. According to one embodiment, illustrated in FIGS. 4 and 5, the means of transfer 14 comprise a gear wheel 114 mounted at least in part pivoting about an axis R of substantially vertical, perpendicular rotation in the plane M, and driven in rotation by a drive means 15, such as a motor 20.
This toothed wheel 114 is disposed in a transfer zone 105, close to of the feed path 9 and the escape route 11, for example adjacent to them.

According to one embodiment, the gripping members 113 present themselves in the form of teeth 113 regularly spaced, for example to the number six, protruding radially from the toothed wheel 114.

When the wheel 114 rotates about its axis R, each tooth 113 describes a circle, passing through a first angular position 6E in which she engages, at the feeding station 109, at least one article 2 from the feeding path 9, and a second angular position OS in which she disengage article 2 at the evacuation station on the escape route 11.

For each tooth 113, we denote 0 its angular position with respect to the axis R of rotation of the toothed wheel 114, this angular position 0 being defined arbitrarily as the angular difference separating a fixed transverse radius r of the toothed wheel 114, and a movable ray r 'passing through the tooth 113.

3o the angular difference between the first and the second angular positions AE, BONE
is for example between 90 degrees and 180 degrees.

According to one embodiment, this angular difference is approximately 120 degrees (Figures 5 and 6).

The transfer speed VT is the tangential velocity of the teeth 113 during the rotation of the wheel 114.

Variations in the transfer rate VT of the tooth 113 as a function of its Angular position A can be defined as follows.

When 8 is substantially equal to 6E, the transfer speed VT is substantially equal to the entry velocity VE of the articles.

In this way, the tooth 113 engages at least two articles 2 continuously, without striking them (FIGS. 4 and 5), forming a batch 4 of grouped articles.
The transfer speed VT then increases continuously with the position angle 6, to reach a value substantially equal to the speed of exit vs.

2o Thus, a space is created between lot 4 and articles 2 again on the way supply 9.

Lot 4 then reaches the evacuation station 111 where it is arranged on the track 11 which supports it at constant speed VS, while the tooth 113 disengages.

According to one embodiment, now described with reference to FIGS.

the toothed wheel 114 comprises a stationary fixed base 117 and a disk rotary 118 called platinum in the following description.

The base 117 and the plate 118 are substantially coaxial with axis R and superimposed, the plate 118 being disposed above the base 117; they define between them a substantially cylindrical enclosure 119.

A localization near the R axis is called inner, as opposed to a remote location of the R axis, said external.

Radial branches 120 arranged in a star are inserted into the enclosure 119 between the base 117 and the plate 118.

Each branch 120 has on the one hand an end 121 facing towards the inside, fixed to the plate 118 by means of a pivot 122 of parallel axis R1 at the axis R, the set of pivots 122 being inscribed in a circle of axis R.

Each branch 120 has on the other hand a free end 123 facing towards the outside, protruding radially from the enclosure 119 to form the tooth 113 described above.

The rotation of the plate 118 about its axis R causes the rotation of the branches 120 in a circular motion of axis R, each branch 120 sweeping in its movement the space defined by the enclosure 119.

2o The pivoting of each branch 120, about its axis R1, relative to the platinum 118, is controlled by a roller 124 or a pin of axis R2 parallel to the axis R, attached to the inner end of the branch 120, away from the pivot 122.
Each roller 124 cooperates with a groove 125 forming a cam, formed in the base 117, in which the roller 124 circulates during the rotation of the platinum 118, this groove 125 being extended in a closed loop around. the R axis of rotation of the toothed wheel 114.

This groove 125 forms in the base a continuous cam track 126, followed by the roller 124 which thus forms a cam follower.

This groove 125 is arranged so that:
when the tooth 113 passes through the feed station 109, the branch 120 which the door pivots in the opposite direction of the rotation of the wheel 114 so that the speed of the tooth 113 decreases until it is substantially equal to the VE entry speed when engaging items; and according to a first embodiment, between the feed station 109 and the evacuation station 111, said branch 20 pivots in the direction of rotation s of the wheel 114 so that the speed of the tooth 113 increases to be substantially equal to the output speed VS, so that the items are grouped in batches, accelerated, spaced apart;
according to a second embodiment, between the feed station 109 and the evacuation station 111, the orientation of said branch 120 being constant with respect to the wheel 114, so that the speed of the tooth 113 increases to be substantially equal to the speed of the gear wheel 114, so that the articles are grouped in batches, accelerated, spaced apart.

The second embodiment is now described in detail.
The cam path 126 has a pseudo-circular shape of axis R, and comprises two related portions:

a first portion 127 of substantially constant curvature, that is to say substantially circular axis R, extending over about a half turn to three quarter turn around the R axis, facing the evacuation station 111 a second portion 128 having a variable curvature, extending over about a quarter of a turn to a half turn around the R axis, and facing the feeding station 109.

The cam path 126 having a radius of curvature p (FIG. 6), recalls that the curvature of the cam path 26 is defined by the inverse 1 / p of radius of curvature p.

In this way:

during the passage of the roller 124 in the portion 127 with constant curvature, the orientation of the branch 120 is substantially constant, the speed VT of the tooth 113 is therefore substantially constant;

during the passage of the roller 124 in the portion 128 with variable curvature, the branch 120 rotates about its axis R1, the speed VT of tooth 113 varying accordingly.

According to an embodiment illustrated in FIG. 6, the portion 128 comprises a first part 128a adjacent to the portion 127 with constant curvature, and extending angularly about a quarter of a turn; and a second portion 128b located near the entry station 109, between the first portion 128a and the portion 127 with constant curvature, and which extends angularly over a few degrees, for example about ten.

The first portion 128a has a substantially increasing curvature tinéairement since the portion 127 with constant curvature until the second part 128b, so as to form a spiral arc axis R.

The second part presents a curvature that has been decreasing since first portion 128a to portion 127 at constant curvature.

In addition, the portion 128 with variable curvature comprises a baffle 129 located at near the feeding station 109, at the junction between the first part 128a and the second part 128b.

When the roller 124 leaves the portion 127 and engages in the first part 128a, this forces it to move away from the axis R, so that the branch 120 pivots in the direction of rotation of the plate 118, the transfer speed VT of the tooth 113 being then increasing (Figures 5 and 6).

The tooth 113 is therefore advanced in relation to the plate 118.

When the roller 124 passes the baffle 129 then engages in the second part 128b, this forces it to get closer to the axis R, so that the plugged 5 120 rotates in the opposite direction of the rotation of the plate 118, the speed of VT transfer of the tooth 113 then decreasing.

The speed VT of the tooth decreases until it is substantially equal to the speed VE input during the passage of the tooth 113 by the feed station 9, for io ensure smooth gripping of articles 2, the pebble then being substantially in the middle of the second pare 128b (Figures 5 and 6).

The tooth 113 thus loses its lead, and lags behind the platinum 118.
ts Finding the circular portion 127, the roller 124 forces the branch 120 at keep a constant orientation with respect to the toothed wheel, so that the VT speed of the tooth 113 increases substantially up to the speed of the wheel tooth 114, substantially equal to the exit speed VS, the articles 2 being grouped in batches 4, accelerated and spaced.

According to the first embodiment, by finding the circular portion 127, the roller 124 forces the branch 120 to pivot about its axis R1 in the direction of the rotation of the plate 118, so as to gradually accelerate the tooth so that its speed VT increases substantially up to the output speed VS, Articles 2 being grouped in lots 4, accelerated and spaced.

In both embodiments, the tooth 113 thus recovers its delay by compared to platinum 118.

3o forming a cam follower, the roller 124 thus makes it possible to regulate the speed of VT transfer of the tooth 113 during the rotation of the plate 118.

The adjustment of the toothed wheel 114 to allow in particular the change of the number of items 2 per lot 4 is made by angularly shifting the base in such a way as to angularly shift the cam path 126:

- in the direction of the rotation of the plate 118 to reduce the number of articles 2 by lot 4; or - in the opposite direction of the rotation of the plate 118 to increase the number of items 2 per lot 4; and by varying the ratio between the speeds of a starwheel 137 (defined below after) and wheel 114.

Thus, for example, to group n successive items, the relative speeds are such as a tooth 113 engages 1 article 2 every n articles 2 advanced by the star wheel 137.

It is thus possible to easily and quickly change the number of articles Batch.

Moreover, in order to facilitate the gripping of articles 2, the teeth 113 are extended in a direction of elevation, and have a surface 130 suitable for follow the form of Articles 2.

According to one embodiment, the teeth 113 have two surfaces opposed outer surfaces 131, 132 curved to conform to the shape of an articie 2 cylindrical, as well as two upper and lower 133 guide surfaces protruding vertically on either side of each branch 120.

3o The guide surfaces 133, 134 are extended tangentially relative to at the wheel 114, and bear respectively on a circumference 135 of the platinum 118 and on a circumference 136 of the base 117, on which they slide during the rotation of the plate 118 relative to the base 117.

In order to order and rate items 2 from the track 9 for positioning and spacing wanted when engaged by the teeth 113, the device 8 may furthermore understand means 18 such as a starwheel 137.

The starwheel 137 is pivotally mounted about an axis of rotation R ' substantially parallel to the axis R of rotation of the toothed wheel 114.

According to one embodiment, illustrated in FIGS. 4 and 5, the wheel starry 137 comprises at its periphery a toothing 138 which meshes articles 2 into from supply path 9, and disengages them at the station 109 to allow their gripping by the teeth 113 of the wheel toothed 114.

For this purpose, the toothing 138 comprises housings 139 able to receive Articles 2, the shape of each dwelling 139 being substantially complementary to an Article 2.

2o In order to ensure a continuous movement of articles 2, the tangential velocity of the star wheel 137, or housing 139, is substantially equal to the speed VE entry.

The rotation of the star wheel 137 can be ensured by a means drive 19 such as a motor 20.

According to one embodiment, one of the motors 20 of the drive means 15, 19, or both, are connected to the control and servo device 16 which is arranged to apply to them a predetermined speed profile.

According to one embodiment, the motor 20 is a motor whose speed of rotation is continuously adjustable, for example an electric motor, Brushless DC type.

We now describe the course of a set of two articles 2 consequential, one 2a being said upstream, the other 2b downstream, intended for the same batch 4, since the station, according to a setting where installation 1 produces packs of four goods (ie two lots of two items).

Both items 2a, 2b are routed along Feed Lane 9 to a constant speed VE to the transfer zone 105 where they are engaged by the star wheel 137 which makes them describe an arc-shaped trajectory of circle, always at a constant speed VE, to the feed station 109.
i0 they are then simultaneously disengaged by the starwheel 137 and engaged by the toothed wheel 114, a tooth 113 engaging with the article 2a upstream to a speed equal to the entry speed VE.

Articles 2a, 2b then undergo a gradual acceleration under the effect of the increase of the speed VT of the tooth 113.

This acceleration has the effect of grouping them into a lot 4, while spacing of the following articles 2, not yet engaged by the toothed wheel 114.

Articles 2a, 2b then describe a substantially shaped trajectory bow circle around the periphery of the wheel 114, for example a quarter of circle, at the end of which they are arranged on the escape route, at a speed equal to the output speed VS.

When changing machine pitch P (which corresponds to the distance separating two batches of consecutive articles), the wheel change is carried out tooth 114, which is replaced:

by a wheel 114 comprising a lower number of branches 120 for an increase of the pitch P; or by a wheel 114 comprising a greater number of branches 120 for a decrease in pitch P.

In conventional installations, where the gripping organs circulate in a constant speed equal to the output speed, it is difficult to increase the cadence without risk of damaging the articles, because of the shocks they undergo during brutal accelerations caused by the gripping organs.

The installation 1, and more particularly the device 8, allow a share the the setting of the production rate C and the setting of the number of items 2 by lot 7 and step P.

It is recalled that the production rate C of the installation 1 is defined as follows: C = P (2) Thus, to act on the cadence C constant pitch P, we can adjust the speed of VS output.

The output speed VS can be adjusted by regulating in particular The operating speed of the drive means 13 of the conveyor 11.
The pitch setting P is related to the setting of the number of items per lot 7. More precisely, the pitch P is an increasing function of the number N of articles per lot 7.

The conveyor system 22 is now described according to a particular embodiment of embodiment with reference to Figures 9 to 18.

This conveying system 22 makes it possible to route the blanks 24 flat along 3o of a transport surface S extending in the plane M, towards the conveyor while placing them next to lots of articles, for example under the lots 7.

It is adjustable, so you can carry 24 size blanks different, depending on the number of items 2 per lot 7 and step P.

For this purpose, the conveyor 23 comprises a plurality of pushers 26 5 regularly spaced, attached to a movable support 55 which defines a path in a closed loop, locally contiguous to the transport surface S.

The pushers circulate continuously, one-way and periodically the along this trajectory, which extends substantially in a plane P of elevation longitudinal, called conveying,.

The support 55 is moved by the driving means 25, slaved to the control device 16, and whose speed can vary so keep on going.
For this purpose, the driving means 25 may comprise a motor 20 to adjustable and / or variable speed of rotation, for example a brushiess motor.
Each pusher 26 is movably mounted between a so-called inactive position where the pusher 26 is located at a distance from the transport surface S and does not not 2o thereof, and a so-called active position where it is at least partially from the transport surface S.

In its active position, the pusher 26 engages with a blank 24 and shoot this one along the transport surface S.
Each pusher 26 can be actuated by a rotary movable member selector 56, engaging the pusher 26 to pass it from its inactive position at its active position.

This selector 56 is set in motion by a drive means 57 whose speed is variable, and for this purpose includes a brushless motor, or any other type of engine whose speed of rotation is adjustable and / or variable of continuous way.

The drive means 57 is slaved to the control device 16, whose memory 17 contains a pre-programmed set of speed profiles not constant, applicable to the drive 57.

The control device 16 is arranged to apply to the means 25 of the actuating member 56 a speed profile such that the operation of the actuating member 56 is periodic, the period of the actuating member 56 being defined as the time interval separating two successive passages of the actuating member 56 by the same position.

In particular, the period of the transporter 23 being defined as the interval of time separating the passage of two pushers 26 by the same point of the trajectory, the control device 16 is arranged so that the period of the actuating member 56 is a multiple of the period of the conveyor 23.
According to an embodiment illustrated in FIGS. 9 and 10, the support 55 is an endless chain meshing with two pinions 58 at least one of which is associated to the engine 20.

In variants not shown, the support 55 is a toothed belt, or a towing cable, or any other equivalent means.

While each pusher 26 is a V-shaped rigid piece which comprises a first branch 59 able to come into engagement with the selector, and a second branch 60 substantially perpendicular to the first.
When the pusher is in the inactive position, this second branch 60 at least in part of the transport surface S to engage with a flan 3o 24.

For this purpose, the second branch 60 comprises a surface 61 which, when the pusher 26 is in its active position, extends in a plane of elevation cross.

The pushers 26 are regularly distributed along the chain 55, on which each is pivotally mounted about a transverse axis 62, forming means for attaching the pusher 26 to the chain 55.
The pushers move along their path by being guided in a rail 63 which extends substantially in a longitudinal elevation plane, under the area transport S, parallel to this trajectory.

lo the rail has an upper zone 64 substantially rectilinear, longitudinal, contiguous to the transport surface S, a lower zone 65, also substantially rectilinear, longitudinal, located at a distance from the surface S
of transport, connected by a first and a second end zone 66, 67, shaped like semicircles.

Along the upper zone 64, the rail 63 separates into two ways: a way upper 68, contiguous to the transport surface S, and a lower channel 69 located under the first track 68.

2o the pusher 26, meanwhile, comprises a first lug 70, salient laterally of the first branch 59, and a second lug 71 projecting laterally from the second branch 60.

The lugs 70, 71 allow both the guiding and the blocking of the pusher 26 in the rail 63.

Near the first end zone 66, the conveyor 23 presents a switch zone 72 where the tracks 68, 69 are interrupted, to allow the pushers 26 to pivot freely about their axis passing from their position inactive to their active position.

The selector 56 is disposed near this switching zone 72.

In order to ensure pivoting of the pushers, the selector 56 comprises a cam 73 extends substantially in the plane P, and rotated in this plane P around a transverse axis.

It is noted at the angular position of the cam 73 in the plane P.

The cam 73 is adjacent to the upper zone 64 of the rail, to come momentarily engaged with the second leg 60 of the pusher 26 of to rotate the latter.
During its rotation, the cam 73 passes through a first angular position al where it engages at least the pusher 26 to rotate it about its axis 62, and a second angular position a2 where it releases the pusher 26.

The conveyor system 22 is provided for the cam 73 to act on a predetermined subassembly of the set of pushers 26 of the conveyor 23.
For this purpose, the operation of the cam 73 is periodic, its period being defined as the time interval separating two successive passes of the cam 73 by the same angular position.

If we define the period of carrier 23 as the time interval separating the passage of two pushers by the same point of the trajectory defined by the chain 55, the period of the cam 73 is a multiple of the period of the carrier 23.

The period of the cam 73 is adjustable by applying to its means 57 a speed profile selected from a pre-programmed set in the memory 17 of the control device 16.

Thus, the cam 73 is provided to actuate a pusher 26 on two, one on three, one in four, or more, so its speed of rotation VC is regulated in result.

It is therefore possible to vary the number of pushers simultaneously in active position.

The speed VC at which the cam 73 is driven by its means 57 is continuous, periodic, and variable depending on the position angular cam 73.

In particular, the speed VC has in particular the following characteristics:
-, it is of constant sign, so that the cam 73 turns one way in the same direction as the chain 55;
it is substantially constant since the first angular position a1 up to the second angular position ct2 of the cam 73;
it is non-constant, for example increasing then decreasing, or inversely depending on the setting, from the second angular position a 2 to the first angular position a1 of the cam 73.

The speed profile of the cam 73 is, for example, chosen from a set 2o speed profiles pre-programmed in the memory 17 of the device of order 16.

In this way, depending on its speed, the cam 73 can engage selectively a number of successive pushers 26 belonging to a sub-predetermined set of all pushers 26.

Three VC speed profiles of the cam 73, depending on its position angular, are shown in Figure 19.

3o The profile shown in solid lines corresponds to a setting of the cam 73 according to which the latter actuates a pusher 26 out of two.

While the profiles represented in mixed and discontinuous lines correspond respectively at two settings in which the cam 73 actuates a pusher out of three, and one in four pusher.

The distance d separating the surfaces 61 from two successive pushers active position is substantially equal to the pitch P of the installation.

Indeed, this distance corresponds to the difference between two successive blanks 24, intended to be arranged next to lots 7 of Articles 2, for example under these, prior to the constitution of the packs 3.

The distance d is therefore a multiple of the distance m between two pushers 26 successive on the channel 55.

This distance m, called module, is fixed during the manufacture of the installation, and in particular of the conveyor system 22.

We now describe a mode of operation of the conveyor device 22, according to a first setting where the cam 73 engages a pusher 26 on two, in 2o reference to Figures 10 to 14.

We follow for this the race of a first, a second and a third pushers 26a, 26b, 26c successive along their path, starting a location where the pushers 26a, 26b, 26c are all in the zone Lower 65 of the rail 63.

The three pushers 26a, 26b, 26c are routed along the lower zone 65, then along the first end zone 66, while being held stationary in rotation in the rail 63, the lugs 70, 71 being in abutment against the edges of the rail.
At the end of the first end zone 66, the first lug 70 of the push 26a, 26b, 26c is guided by the lower path, while the second ergot is guided by the upper way 68.

The pushers 26a, 26b, 26c are then all three in their inactive position.
When the first pusher 26a opens into the switching zone 72, its second branch 60 stops against the cam 73, the latter being in its first angular position al. The cam 73 then forces the pusher 26a to swing around its axis (Figure 11).

Under the action of the cam 73, which accompanies at constant speed the first push 26a, the first lug 70 is directed to the upper track 68, the second branch 60 protruding from the transport surface S upwards, for engage with a blank 24 (Figure 12). The first pusher is then in her active position.

When the cam 73, in the second angular position a2, disengages the first pusher 26a, the latter is held fixed in rotation, its second pin 71 being guided by the upper track 68 of the rail along the surface S
of transport.

The cam 73 then accelerates, pivoting about its axis. Meanwhile, the 2o second pusher 26b travels the referral zone 72 while remaining in its inactive position (Figure 13).

Then the cam 73 decelerates to regain its first angular position a2, and engage the second pusher 26c in the same manner as the first pusher 26a (Figure 14).

Each pusher 26 pushes a blank 24 to the conveyor 11. After the blank was taken in charge by the conveyor 11, the pusher 26 takes up its position inactive in the second end zone 67 of the conveyor 23, for example by pivoting by gravity about its axis.

For this purpose, the rail -63 comprises an auxiliary channel 74 opening into the transport surface S, connecting the latter to the second end zone 67.

Near this end zone 67, the auxiliary channels 74, upper and lower 69 are locally tilted down to force the push 26 assets to move away from the transport surface S and clear the blanks 24.
s According to a second setting where the maximum rotational speed of the cam 73, it can engage one pusher 26 of three. This mode of identical to the one just described, is illustrated on the Figures 15 to 18.
io Of course, one can adjust the rate of the installation 1 by increasing simultaneously and progressively the rotation speeds of all training means.

This is made possible by the use of rotational speed motors adjustable or variable continuously, combined. using a device for ordered and enslavement able to synchronize the training means and their apply speed profiles already programmed in memory.

Claims (27)

1. Packaging facility form finished products such as packs from batches (7) of articles (2), which includes:

a conveyor (11) capable of receiving the batches (7) of successive articles (2) for forward them from a so-called upstream location to a so-called localization downstream, the upstream faces of two successive batches (7) being spaced apart by predetermined distance said step (P);
- an advancement lane (9) along which articles (2) are routed one by one towards said conveyor (11) being juxtaposed to each other;
means for transferring (14) articles (2) from the advancement path (9) to the conveyor (11), able to take and group the articles (2) for forming spaced batches (7); and a transporter (23) capable, on the one hand, of conveying one by one of the blanks (24) in carton or equivalent, laid substantially flat on the conveyor (23), to said conveyor (11), and arranging the blanks (24) on the conveyor (11) in look at lots (7) of items;
- drive means (13) of the conveyor, (15) means for transfer and (25) carrier, characterized in that it comprises a control device (16) and servo-control means (13, 15, 25) adapted to apply to each drive means (13, 15, 25) a speed profile selected from a pre-programmed set of speed profiles, to allow adjustment of the (P) and / or the number of items (2) per lot (7) depending on the step and / or type of lot desired. 2. Installation according to claim 1, characterized in that the said carrier (23) comprises pushers (26) of the blanks (24) arranged successively on the conveyor (23), each pusher (26) being adapted to come engaged with a blank (24) to convey it to the conveyor (11), the distance between two successive pushers (26) engaged with a blank (24) being predetermined and substantially equal to the pitch (P). 3. Installation according to claim 2, characterized in that it comprises in in addition to means (57) for adjusting the distance between two pushers (26) successive contacts with a blank (24) according to a predetermined predetermined value among a group of pre-programmed values, all multiples of the same value called module (m). 4. Installation according to one of claims 2 or 3, characterized in that each pusher (26) is movably mounted between a so-called inactive position where the pusher (26) is located at a distance from the transport surface (S) and protrudes not of this one, and a so-called active position where it concerns at least partially from the transport surface (S) for engaging an object and pushing it this along the said surface (S), so that the number can be varied of pushers (26) simultaneously in the active position. 5. Installation according to one of claims 2 to 4, characterized in that what includes:
- Drive means (25) of a movable support (55) of the pushers;
a movable member (56) for actuating the pushers (26) to make them move from their inactive position to their active position at the area transport ;
- Drive means (57) of said actuating member (56). 6. Installation according to claim 5, characterized in that the device of control (16) is arranged to apply to the drive means (25) of the actuating member (56) a speed profile such as the operation of the actuating member (56) is periodic, the period of the organ actuator (56) being defined as the time interval separating two successive passages of the actuating member (56) by the same position. 7. Installation according to one of claims 2 to 6, characterized in that the carrier period (23) being defined as the time interval separating the passage of two pushers (26) by the same point of the trajectory, the control device (16) is arranged so that the period of the organ actuator (56) is a multiple of the period of the conveyor (23). 8. Installation according to one of claims 2 to 7, characterized in that each pusher (26) is in the form of a rigid piece which comprises a first branch (59) adapted to engage the organ drive (56) and a second limb (60) substantially perpendicular to the first, able to protrude at least partly from the surface (S) transport to engage a blank (24). 9. Installation according to one of claims 2 to 8, characterized in that each pusher (26) comprises an axis (62) substantially perpendicular to the plane (P) for conveying, forming means for fixing the pusher (26) to the support (55), and around which the pusher (26) is pivotable, to pass from its inactive position to its active position, or vice versa. 10. Installation according to one of claims 2 to 9, characterized in that the conveyor (2) comprises a guide rail (63) which extends substantially in the conveying plane (P), substantially along the defined path by the support (55), said rail (63) including, substantially along the surface (S) transport, a first said upper channel (68) for guiding the pushers (26), contiguous to the transport surface (S), and a second track (69) said lower guide pusher (26), parallel to the first. 11.Installation according to claim 10, characterized in that each pusher (26) comprises at least one first lug (70) projecting from the first branch (59) substantially perpendicular to the conveying plane (P), suitable to cooperate with the lower channel (69) when the pusher (26) is in position inactive, and with the upper track (68) when the pusher (26) is in position active. 12.Installation according to claim 11, characterized in that each pusher (26) further comprises at least one second lug (71) projecting from the second branch (60) perpendicular to the conveying plane (P), suitable to cooperate with the upper track (68) when the pusher (26) is in position inactive. 13. Installation according to one of claims 10 to 12, characterized in that that the carrier (2) has a so-called switching zone (72) where the rail (63) of guiding is interrupted, and in which the pushers (26) are adapted to swing around their axis (62) to move from their inactive position to their position active. 14.Installation according to claim 13, characterized in that the organ actuator (56) comprises a cam (73) extended substantially in the conveying plane (P) close to said switching zone (72), and driven in rotation in this plane about an axis substantially perpendicular to that this by said driving means (25), passing through a first position angular (.alpha.1) where said cam (73) engages at least one of the pushers (26) to rotate it about its axis from its inactive position to its active position when passing through the switch zone (72), and a second angular position (a2) where said cam (73) releases the pusher (6). 15.Installation according to one of claims 5 to 14, characterized in that the velocity profile is selected from a pre-programmed set of such that the actuating member (56) selectively engages a number of successive pushers (26) belonging to a subset predetermined set of pushers (26). 16. Installation according to one of claims 1 to 15, characterized in that the transfer means (14) comprise a rotatable member adapted to take grouping the articles (2) to form spaced batches (4), said organ rotary comprising a succession of gripping members (113) arranged for engaging items (2) at a feeding station (109) and disengaging them at a evacuation station (111), driven continuously along a closed path, at a so-called transfer speed (VT), greater than or equal to the input speed (VE) the transfer means (14) being arranged so that the transfer speed (VT) gripping members (113) are non-constant, such that:
- when the articles (2) are engaged, the speed (VT) of the gripping (113) is substantially equal to the entry speed (VE);
during the transfer of the articles (2), the speed (VT) of the prehension (113) is greater than the input speed (VE);
when the articles (2) are disengaged, the speed (VT) of the gripping (113) is substantially equal to the output speed (VS). 17. Installation according to claim 16, characterized in that the articles (2) are driven continuously along said closed path along a path who at least a quarter of the periphery of the rotary member, so that the grippers (113) can come into contact with the articles and the group in successive batches, the speed of the rotary member being greater than the entry speed (VE) of the articles and the rotary member vary the number of articles per batch. 18. Installation according to claim 17, characterized in that the organ rotary transfer means (14) comprises a toothed wheel (114) a part of which (118) is pivotally mounted about an axis (R) of rotation, this wheel (114) being disposed near the feed path (9) and the track discharge (11), this wheel (114) comprising said gripping members (113). 19.Installation according to one of claims 16 to 18, characterized in that said gripping members (113) are in the form of teeth (113) substantially regularly spaced radially projecting from the gear wheel (114), each tooth (113) describing a circle through a first angular position (.theta.E) in which it engages at least one article (2) feeding station (109), and a second angular position (.theta.S) in which it disengages the latter at the evacuation station (111). 20.Installation according to claim 19, characterized in that the difference angle between the first and the second angular positions (.theta.E, .theta.S) is between 90 and 180 degrees. 21.Installation according to claim 18 to 20, characterized in that the said toothed wheel (114) comprises a fixed base (117) circular and a disk (118), coaxial and superimposed, between which are arranged radial branches (120) whose free ends (123) form the said teeth (113). 22. Installation according to claim 21, characterized in that the said branches (120) are rotatably mounted on the rotating disc (118) by means of pivots (122) with axes (R1) parallel to the axis (R) of the toothed wheel (114). 23.Installation according to claim 22, characterized in that each branch (120) comprises a roller (124) or a lug which cooperates with a groove (125) formed in the base (117), this groove (125) being extended in a loop closed around the axis (R) of rotation of the toothed wheel (114). 24. Installation according to claim 23, characterized in that the said throat (125) is arranged so that:
when the tooth (113) passes through the feed station (109), the branch (120) which the door rotates in the opposite direction of the rotation of the wheel (114) so that the speed (VT) of the tooth (113) decreases to substantially equal to the entry speed (VE) when engaging the articles (2);
between the feed station (109) and the evacuation station (111), the orientation of said branch (120) is constant with respect to the wheel (114) for the speed (VT) of the tooth (113) to increase to be substantially equal to the speed of the wheel (114), so that the articles (2) are grouped in batches (4), accelerated, spaced. 25. Installation according to one of claims 16 to 24, characterized in that what further comprises means (18) arranged near the station feeders, able to order and clock articles (2) from the feed path (9), so that they present the positioning and the desired spacing at the moment of their grip by the means of transfer (14). 26.Installation according to claim 25, characterized in that the means (18) to order and cadence the articles come in the form of a star wheel (137) pivotally mounted about an axis of rotation (R '), comprising at its periphery a toothing (138) capable of meshing and disengaging the articles (2), the toothing (138) having housings (139) suitable for individually receive the items (2), the tangential velocity of the said wheel stellate (137) being substantially equal to the input speed (VE). 27. Installation according to one of claims 16 to 26, characterized in that what comprises a drive means (19) for said star wheel connected to the control device (16).